Stabilizer for controllers or regulators



June: 1, 1943; F. D. BURNS EI AL STABILIZER FOR CONTROLLERS OR'REGULATORS Filed May 16, 1940 4 Sheets-Sheet 1 Haj.

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June 1, i943. F. n. BURNS E'l "AL STABILIZER FOR CONTROLLERS OR REGULATORS Filed May .16 1940 4 Sheets-Sheet 2 E 5 WW n T m 7 E W E Qwv f X F Q Y M B d. M m a. M f l mm 1 m M m M b Wm H m m n w h 0 we m ...Q. m .a 4 M: m m a 8 6 J H K June 1, 1943. F. D. BURNS ET AL STABILIZER FOR CONTROLLERS OR REGULATORS v Filed May 16, 1940 4 Sheets-Sheet 5 IN VENT 0R5.

m m Wm 50 m x/ Patented June 1, 1943 STABILIZER FOR CONTROLLERS OR REGULATORS Frank Donald Burns and Warren B. Thorne, Michigan City, Ind., assignors to The Rays Corporation, Michigan City, 11111., a corporation of Indiana Application May 16, 1940, Serial No. 335,542

'7 Claims.

This invention relates to a stabilizer for controllers or regulators, and more particularly to the provision of a stabilizer with a controller or regulator for a process being controlled, for example acombustion system.

The primary object of the invention is to provide simple and inexpensive means for rapidly and eifectively stabilizing the action of a controller or regulator.

A further object is to provide a device of this character which reduces to a minimum the changes in the setting of a controller or regulator required to effect changes in the process being controlled responsive to variations in operating conditions of the controlled process.

A further object is to provide a stabilizer whose action incident to a change in the setting of a controller or regulator may be adjusted to correspond to the inertia or lag in the process being controlled and thereby reduce to a minimum the operations of the controller.

A further object is to provide means for creating a pneumatic pressure variation in a stabilizing chamber and associated pneumatic system connected with the metering unit of a regulator, incident to the operation of the regulator, and associated means for permitting said pressure variation to bleed oil in the control system.

A further object is to provide a device for effooting a change in a controlled process very quickly, and for minimizing or preventing hunting of the controller or regulator at all times.

A further object is to provide a regulator having a slack diaphragm type of metering device with a stabilizer creating pneumatic pressure conditions exerted on the diaphragm at the metering side thereof.

it iurther object is to provide a stabilizer which is usable with regulators actuated by variations in diiferential pressure, or pressure or suction, or flow in a controlled process.

A further object is to provide a stabilizer usable with regulators for controlled process having substantial storage or capacity lag, and/or for controlled systems having excessive pulsations and negligible storage lag.

A further object is to provide a regulator with a stabilizer effective to neutralize inertia in fluid connecting lines, diaphragm chambers, and the like.

Other objects will be apparent from the description and appended claims.

In the drawings:

Fig. l is a. diagrammatic view illustrating one application of the invention to a regulator or con-- troller connected with a process having predominant storage lag to be controlled, for response to variations in differential pressure or flow in said process.

Fig. 2 is a diagrammatic view illustrating the application of our invention in a controller or regulator connected to a process having predominant storage lag, for response according to variations in suction or draft in said process.

Fig. 3 is a diagrammatic view illustrating our invention applied in a regulator or controller for a process having predominant storage lag, wherein said controller is responsive to variations in pressure in said process.

Fig. 4 is a chart illustrating the operation of the device illustrated in Fig. 1 where the same has been adjusted to give dead beat regulation.

Fig. 5 is a chart similar to Fig. 4, and illustrating another condition of operation of the de vice illustrated in Fig. l. s

Fig. 6 is a diagrammatic view illustrating a modified embodiment of our invention applied to a regulator for a. process having predominant metering lag to be controlled, wherein the regulator operates responsive to variations in flow or differential pressure in said process.

Fig. 7 is a diagrammatic view of a modified application of our invention. to a controller connected for operation responsive to variations in pressure in a process having predominant met-ering lag.

Fig. 8 is a diagrammatic view illustrating a modified application of our invention to a regulator or control connected to a process having predominating metering lag for operation responsive to variations in suction or draft in said process.

Fig. 9 is a diagrammatic view of another modi fied embodiment of our invention.

Fig. 10 is a diagrammatic view of still another embodiment of our invention.

Before describing our invention, attention is directed to the fact that most processes, such as combustion processes etc, are subject to both metering lag and storage or capacity lag. Hence it is customary to provide a regulator which will compensate for the type of lag which is predominant in the particular process to be controlled. As used herein, the terms metering lag and storage lag will be understood to have the following definitions: Metering lag is the time lag in the control system occurring between the metering unit of the control system and the point at which the fluid connection for said metering end of rod H! at 24'.

unit is tapped with the process to be controlled, and also includes lag induced by'inertia of methe metering unit. Storage lag is the time lag in the process to be controlled occurring between the control element therefor, such as a damper in a stack, and the point of the process at which'the fluid connection to the metering unit is tapped.

Referring to the drawings, and particularly to Figs. 1, 4 and 5 thereof, the numeral l desi nates a metering unit comprising a housing having a slack diaphragm |2 therein dividing the housing into two substantially equal compartments. The margin of the diaphragm I2 is rigidly clamped between complementary parts of the housing, and the intermediate portion of the diaphragm I2 is reinforced by a pair of metal plates |3 secured in face engagement therewith. An opening I4 is formed centrally in the housing at one side thereof, and this opening is closed by a suitable slack diaphragm IS. The opposite side of the housing includes, an offset portion l6 defining a chamber I! which is sealed from the main body of the housing H by a slack diaphragm |8. A rod l9 extends transversely of the diaphragms I2. I and I8. and each of said diaphragms is rigidly secured to said shaft at spaced points along the length thereof, said connections being such that no leak is permitted in any of the three diaphragms or between the following: chamber IT, chamber 20 between diaphragm l8 and diaphragm l2. and chamber 2| between diaphragm 2 and diaphragm l5. A suitable projection or arm 22 is carried by casin at the side thereof adjacent opening |4 through which the rod l9 projects. This arm 22 has pivoted thereto at 23 a weighbeam 24 whose upper end is pivotally connected with the outer The lower free end of the weighbeam 24 carries a magnet 25. A tension spring 26 is connected with an intermediate portion of the weighbeam 24, and is suitably connected by an operating element, such as a master steam meter, in the system to be controlled. It will be understood, of course, that other means than a spring may be utilized as a loading means for applying force responsive to a change in the process to be controlled.

-A pair of mercury switches 21. and 28 or other suitable electric contacts are positioned on opposite sides of the ma net 25 or a common contact in equi-spaced relation thereto when the weighbeam is in neutral position, said mercury switches each being positioned in the path of pivotal movement of said weighbeam. Each of these switches is connected by suitable electric connecting lines 29 with a power member 30, here illustrated as a motor. I

It will be understood, of course. that any suitable power member, or positioning member which may be found desirable, may be employed. The power member 30 serves to operate a shaft 3| which carries an arm 32 fixed thereon. A link'33 is pivotally connected to the arm 32 and constitutes a connecting rod between arm 32 and a piston 33 mounted in a cylinder 34. One end of the cylinder 34 is preferably open to atmosphere. Shaft 3| also rigidly mounts a lever arm 35 which is pivotally connected with a member 36 adapted for control of some element of the process to be controlled. For example, the link 36 may serve to operate a valve or a rheostat in the process being controlled.

The closed end of cylinder 34 has a tube 31 connected thereto, and this tube 31 leads $0 8- chanical parts directly controlled or operated by T-fitting 33 connected in a. line 33. One end of;

the line 33 leads to a stabilizlngchamber 43, and the other end of line 33 communicates with chamber ll of the metering unit I3. The stabilizing chamber 40 has a. conduit 4| connected therewith, and an adjustable valve 42 is interposed in conduit 4|. The outer end of conduit 4| is preferably open to atmosphere.

A conduit 43 serves to connect the chamber 20 of the metering unit H] with the high pressure side of the process to be controlled, and a conduit 44 serves to connect the chamber 2| of the metering unit with the low pressure side of the process to be controlled. The conduits 43 and 44 constitute differential pressure connections, and are preferably disposed on opposite sides of an orifice plate in a conduit or duct of the process to be controlled, as is well understood in the art.

The operation of the device will be explained as applied to a fan for regulating the air flow from a turbine driven fan wherein the speed of the turbine and fan (not shown) 'are' controlled by the throttling steam valve (not/shown), of the turbine. In this connection, it will be understood that the conduits 43 and 44 are connected with the air duct at opposite sides of an orifice plate therein to measure the air flow in the duct by measurement of thepressure dif-' ferential on opposite sides of the orifice. In this application of the invention, when the loading of the sensitive diaphragm of metering unit ll is increased by additional tension in spring 26,

or the relation between diaphragm l2 and spring 26 is otherwise unbalanced, as by a change in the differential pressure in the lines 43 and 44. the weighbeam is operated to swing the magnet 25 toward the right, as viewed in Fig. 1. As the magnet 25 approaches the mercury switch 23, it serves to actuate said switch and thus close one of the operating circuits for the electrical power member 30. The member 3|! rotates the shaft 3| in counterclockwise direction as best illustrated in Fig. 1 to operate the link 36 controlling the throttle valve. At thesame time, the rotation of shaft 3| also swings arm 32 in counterclockwise direction and thus forces the piston 33 to move Within cylinder 34, for the purpose of increasing the air pressure within the cylinder 34, stabilizing chamber 40, lines 31 and 39, and chamber ll of the metering unit. The increase in pressure in chamber H of the metering unit acts upon the diaphragm l6 and its effect is transmitted through the rod I! to the weighbeam 24 to'balance the spring- 26, swing the weighbeam to neutral position, render the magnet 25 inoperative with respect to the switches 21 and 28, break the contact in switch 28, and stop the power member 30. It will thus be seen that the movement of controller 36 produced by the operation of the metering unit is only of proportional duration, since the metering unit itself is counterbalanced to stop the power member which operates the controller 36 in a time proportional to the deviation of a variation from a set point or standard. This substantially stabilizes the throttle valve against overrunning if dead beat regulation is desired, or if hunting" 43 and 44 immediately after the throttle valve has been opened to its new position or setting. However, the speed of the turbine and fan increase responsive to the new position or setting of the controlling means therefor and the differential pressure in lines 43 and 44 likewise increased to make the diaphragm l2 exert increasing force on the weighbeam 24 in the same direction as the stabilizing diaphragm ll, thus supplementing the action initiated by the increased air pressure within chamber ll of the metering unit. During the period required by the turbine and fan to attain the speed corresponding to the new throttle valve setting, the bleed valve 42 in conduit 4| permits the pressure within the stabilizing chamber 40 to bleed off! The adjustable character of the bleed valve permits this bleeding of pressure from the stabilizing chamber 40 to occur at the same or a lower rate of speed than that of the increase in the diil'erential across the main diaphragm i2. Thus it is possible to adjust the valve 42 so that the turbine and fan will reach their new speed corresponding with the setting of the throttle by member 38 at the same time the pressure in the stabilizing chamber 40 and its connected system, i. e. cylinder 34, chamber i1 and lines 31 and 39, becomes atmospheric. In this way, the decrease in the pressure in chamber i1 during the "bleed" action is complemented by the increase in pressure in chamber 20 incident to the increasing difierential in lines 33 and 34.

When the pressure in stabilizing chamber 40 and its connected system becomes atmospheric, the forces then acting upon the weighbeam 24 are the same as at the beginning of the operation. Namely, the tension of spring 28 acting in one direction, and the forces exerted upon the diaphragm i2 and transmitted thereto by the lines 43 and 44 in opposition to the tension of spring 26, are balanced.

When the tension on the loading spring 2 is decreased, as when turbine and fan speed are to be decreased, the operation is the reverse of that above described, with the weighbeam 24 swinging to a position adjacent switch 21 for the purpose of actuating the power member 30 in a direction, such as a clockwise direction as illustrated in Fig. l, to move the members 35 and 36 controlling the throttle valve toward closing position. At the same time, the arm 32 on shaft 3| is also moved in clockwise position as viewed in Fig. 1, thus drawing the piston 33 toward the outer end of the'cylinder and creating a decrease in pressure in the cylinder 34, stabilizing chamber 40,

chamber i1 and lines 31 and 39 below atmospheric pressure. This sub-atmospheric pressure in the system, and particularly in chamber [1, acts upon the stabilizing diaphragm II to shift the weighbeam 24 to neutral position, and thereby again stop the operation of the power member 32 by breaking contact in switch 21. Thereupon, the bleed valve 42 permits the stabilizing chamber 40 to take in air, to again neutralize the pressure in the stabilizing chamber 40 and its connected system at atmosphere.

The operation of the device may be adjusted entirely by adjusting the setting of the bleed valve 42. Thus, for example, the valve may be adjusted to give dead beat regulation as shown in the graph, Fig. 4. From this graph it will be noted that upon an increase in-the tension exerted on spring 28 at time a, the throttle valve is moved by member 36 under the control of power member 80 until time b, when the stabilizing pressure developed in the cylinder I4 by piston II is transmitted to chamber ll of the metering unit and acts against the stabilizing diaphragm "to restore the weigh beam 24 to neutral position. The position of the throttle valve and of power unit 84 then remains constant until time d, by virtue of the comple mentary effect of increasing differential pressure from lines 43 and 44 and decreasing pressure in the stabilizing system incident to the "bleed through valve 42. The time 0 marks the point at which the metering unit is again influenced solely by the main diaphragm l2 and the loading spring 26. Operation of the turbine and fan may then continue constant from time c to time d, at which latter time the tension on spring 28 is decreased, causing the power member 30 to operate the members and ll for control of the throttle valve in closing direction until a reduction in pressure occasioned by operation of the piston 33 in cylinder 24 is transmitted to the metering unit chamber H to cause the stabilizing diaphragm II to act in opposition to the original actuating condition and thereby again restore the weigh beam 24 to neutral position. The resulting change in the differential pressure extends from time d to time I, during which interval the bleed of air into the stabilizing chamber and connected system occurs. Thus, beginning at time ,f, the stabilizing system is inoperative, and the regulator is again restored to control solely by the main diaphragm i2 and loading spring 26.

A slightly different operation can be achieved by varying the proportion or setting between the cylinder 34 and stabilizing chamber 40, so that the throttle valve actuated by the members 35 and 38 responsive to'the movement of the power member may overtravel, and thereafter return to final position in one or two movements. The graph of such a setting is illustrated in Fig. 5, wherein the power'unit is set to move between times a and b, and then remain constant to time c, during which interval the pressure in the stabilizing system falls oil. A reversing operation of the regulator occurs at time c to reposition the throttle valve at a reduced feed setting, in connection with which the pressure in the stabilizing system falls below atmosphere as above explained between time c and d, followed by a period of operation of the power unit at the reset position between times d and c. There then follows a new setting of the power members in increasing direction between times e and f. The differential pressure will thus be seen to increase until it exceeds the desired setting at time c, whereupon it returns in a gradual movement to the desired differential at time I. The two graphs illustrate that the stabilizing system on the control or regulator can be adjusted by means of adjustment of valve 42 to permit the regulator to change the speed of the turbine and fan very quickly. Also, though the throttle valve may be observed to fhunt, the hunting amplitude diminishes with each cycle and the regulator may be said to be stable.

In Fig. 2 embodiment is illustrated a modifled application of our invention, connected with the suction or draft line of a process to be regulated. In this and each of the other drawings, the parts corresponding to those shown in Fig. 1 are designated by the same reference numerals. It will be noted particularly that the metering unit," in this device comprises merely the main diaphragm casing containing the diaphragm l2 which divides the casing l| into opposed chambers 26 and 2|. One side of the casing has the central opening l4 receiving the atmospheric diaphragm II, which is preferably or negligible area, and the rod I! is rigidly secured to both diaphragms l2 and II in spaced relation. In this embodiment, the line 36 between the stabilizing chamber 46 and the metering unit 66 communicates directly with chamber 26 of the wit. A draft or suction line 6| extends from the process to be controlled for communication with the chamber 2| of metering unit 66, and the adjusting spring 26 is positioned to be normally in' opposition to the force exerted upon diaphragm |2 by the suction in line II. The stabilizing chamber 46 has a conduit 4| open to atmosphere and controlled by bleed valve 42. Likewise all other parts of the Fig. ,2 device, in-- cluding the switches 21, 26, the weigh beam 24 carrying a magnet 26, the power member 66, the controller 66 for the system to be operated, and the piston and cylinder arrangement'are the same as in the preferred embodiment.

- In operation, when a setting of the device cocurs under the influence of the spring 26 to operate the power member 66 in increasing direction, the stabilizer generates and transmits to the metering unit 56 through line 26, a pneum'atic pressure which acts upon the diaphragm i2 in opposition to the spring 26 and in complementary relation to the suction in the line 5|, so as to permit the combined pressure in chamber 20 and suction in chamber 2| quickly to stabilize any increase in tension in spring 26. Likewise, upon reverse operation, by an increase in suction in line 6| which overbalances spring 26, the device is operated to close the circuit in decreased pressure direction at switch 21, and thereby operate the power member and stabilizer to reduce to a point below atmosphere the air pressure within the stabilizing system. The suction is transmitted to chamber 26 and complements spring 26 in opposition to the suction in line which initiated the actuation of the regulator.

The Fig. 3 embodiment of the invention illustrates a metering unit 60 of the same type asunit 66, but wherein the chamber 26 of the unit has a direct connection with a line 6| to a pressure source within the process to be controlled. The line 35 from the stabilizing system communicates with the chamber 2| of the metering unit for opposed relation to pressure line 6|. All

other parts of the system are substantially the same as the Fig. 2 embodiment, and bear the same reference numerals by which the same parts have previously been identified herein.

The operation of the stabilizer in this embodiment will readily be understood as follows: An increase in 'the tension of spring 26 to overcome the balance normal between the same and the pressure in line 6| as applied to the diaphragm l2, serves to swing the weighbeam 24 and magnet 25 for closing the increase switch}! to move the power member in increase direction 1, 2 and 3, the regulator may be operated to quickly shift the control element of the process being regulated, and the stabilizer unit simultaneously comes into play to quickly stop the regulator and the control elementof the system being regulated before the latter reaches speed or other condition for which its control has been set. Thus the stabilizer compensates for the storage or capacity lag which may be inherent in the nature of the process being regulated and stabilizes the operation of said process. In each of these embodiments, the slack diaphragms |2, I6 and I6 are so connected that the slack is removed by pressure on the metering side of the diaphragm. This is .quite important in a device of this character, since it the slack were allowed to "billow" with changes in pressure in the metering unit, especially when close to zero, the suitability of the stabilizer would be somewhat impaired, though it would still be satisfactory for some purposes.

In the embodiment illustrated in Fig. 6, a metering unit 16 of the same type-as illustrated in Figs. 2 and 3, is employed in connection with and to simultaneously create a sub-atmospheric pressure in the stabilizing unit. The sub-atmospheric pressure or suction acts upon the diaphragm l2 in opposition to the spring 26, and serves to complement the pressure exerted upon diaphragm |2 through line 6|, and thus to reestablish balanced condition of the weighbeam.

It will readily be seen from the 'above that in each of the embodiments illustrated in Figs.

a differential pressure application wherein line 1| constitutes the high pressure connection, and line 12 constitutes the low pressure connection with the process being regulated. Furthermore in this arrangement, the stabilizing chamber 40 of the previous embodiments is entirely elimihated, and the conduit 31 leading from the stabilizing cylinder 34 is connected directly with the conduit 1| and 13. A stabilizing adjustment valve 14 is interposed in the high pressure line 1| and the dampening valve 15 is interposed inthe line 12. Thus when the system is used to regulate air flow through a duct or boiler, the air flow being controlled by a damper connected with controller 36 and being measured by a suitable differential pressure means such as an orifice plate in the duct, the following operation occurs: When more air flow is required, the tension on spring 26 is increased by external means constituting a part of the processto be controlled, and shifts the weighbeam 24 in increasing direction to position its magnet 25 in operative relation to increase switch 28. This closes a circuit to'the power member 36 for operation thereof in increase direction, for example, clockwise direction. At the same time, the arm 32 is operated by the power member 36 to operate the piston in cylinder 34 to increase the pressure therein and apply said pres- .sure to the line 1| and the chamber 20 of the metering unit, to complement the pressure in line 1| and thus again establish a balanced relation of the diaphragm I2 as against the setting of the spring 26 which initiated the operation. The valve 14 in the high pressure connecting line 1| is set in partially closed position as desired, so that the air flow therethrough incident to the increase in air pressure supplied from cylinder 34 by line 31 is slow. However. the excess or preloading pressure from cylinder 84 is soon dissipated through valve 14, and the pressures in thediaphragm chambers 20 and 2| return to the true pressures in the process to be controlled. In cases where the processes are pulsating excessively, both chambers 14 and 15 may be partially closed to dampen out the pulsations and thus prevent excessive operation of the metering unit 16 and of the power unit 30. However this valve positioning will not add any metering lag to the regulation.

The device willoperate satisfactorily even when metering lag is interposed in the line 12 as by partial clogging thereof with duct or foreign matters. In some instances, the lines 1| and 12 will be of great length, and hence the inertia of the columns of air in these lines becomes additive to the inertia of the diaphragm and its connecting mechanism. It will be noted that the air in line 1| beyond point 13 moves in a single direction after the contact has been made, and does not have to reverse when the diaphragm moves to balance the spring 26 and break the circuit to the power member 30. Thus the inertia of the column of air in one line has been eliminated and only the inertia in the other line 12 is effective. However, since added power is available, the effect of this inertia, in line 12 is practically neutralized.

The Fig. '7 embodiment utilizes a metering unit 80 of the same type as unit 10, having a pressure line 8| connected with the chamber 20, and having line 31 from cylinder 34 connected with line 8| at 82. An adjustable bleed valve 83 is interposed in line 8| at the side of connection 82 opposite the metering unit. The operation of this device will be readily understood from the previous description of the Fig. 3 embodiment, and it will be seen that this arrangement permits the positive pressure in the stabilizing cylinder 34 to be additive to the pressure in line ill for the purpose of counter-balancing spring 26, or to be negative pressure which subtracts from the pressure in line 8|, if the latter initiated the operation of the regulator.v

The embodiment illustrated in Fig. 8 utilizes a metering unit 90 similar to units 10 and 80. In this embodiment, a. suction or draft line 9| is connected for communication with chamber 2|, and in turn has line 31 from stabilizing cylinder 36 connected thereto at point 92. Adjustable bleed valve 93 is interposed in Lne 9| remote from metering unit 90 with respect to point 92. The operation of this embodiment will be readily understood, particularly with respect to the embodiment illustrated in Fig. 2. Specifically, when draft is to be increased, operation of the regulator is initiated by spring 26 and a suction will be created by stabilizing cylinder 34 to complement the suction in line 9| for the purpose of quickly balancing the spring 26. In instances where the draft is to be lowered, a positive pressure is created in line 31 to reduce the efiect of the initial suction in line 9| to a point in balance with the setting of spring 26.

In each of the Fig. '1 and Fig. 8 embodiments, the use of a single fluid pressure line from the unit to be regulated and the connection of the stabilizer with said line completely neutralizes the inertia of the air in said line, and hence rene ders the device rapidly responsive despite existence of metering lag incident to the length of the line to the metering chamber. Also, in each of these embodiments, the bleed valves 83, 93, respectively, may be set to eliminate the undesired pulsations in the process to be controlled.

While the stabilizing system has been herein described and illustrated in connection with pneumatic devices. it is not confined thereto and with obvious changes in small mechanical details to correspond to the type of systems desired, it may be rendered applicable to systems or processes operating on fluids of any nature.

Also, although a diaphragm type of metering unit has been described and illustrated, any other type of measuring and regulating unit may be stabilized by apparatus including the stabilizing system herein described.

The Fig. 9 embodiment of the invention illustrates the manner in which the same may be used in a non-electrical system. In this application a weighbeam I is pivoted on a suitable support at IOI, and is acted upon by a suitable loading element here shown as a weight I02. The end or weighbeam I00, opposite loading element I02, has a connection I03 with an inverted bell I04 extending into a liquid container I05. A suitable line I06 extends upwardly through the container I05 and beneath the bell I04 at I01, and the opposite end of line I06 communicates with a duct I08 in the process to be controlled. In this embodiment it will be seen that the metering unit constitutes an inverted bell which acts upon the weighbeam in opposition to the loading element I02 in substantially the same manner in which the metering element, weighbeam and loading element cooperate in the previous embodiments.

A suitable four way valve I09 has its plunger connected by shaft IIO with the weighbeam I00 on the side thereof ad acent the loading element I02. The valve plunger III is of a type to control a flow of compressed air or other actuating fluid supply from line II2 selectively to lines I I3 or H4. A drain by-pass H5 is provided in the valve I09 and a drain line II6 extends from the lower end of the valve I09. A power cylinder II1 has line II3 connected'at one end thereof and line II4 connected at the other end thereof. The piston II8 is mounted on a rod II9 which is connected with suitable linkage I for operating a. control element in the process to be controlled, which control element may constitute a damper I2I. An arm I22 extends from the shaft I I9 of the power piston and carries a stabilizing cylinder I23 which is shiftable therewith. A stationary fluid line I24 mounts a stationary piston I25 having an opening therethrough communicating with the line I24. It will thus be seen that if the power piston H8 is operated, the cylinder I23 is caused to shift relative to the stationary piston I25 and thereby create a stabilizing pressure condition. Line I24 extends to and communicates with a stabilizing chamber I26 which is in turn connected to a line I21 which extends into a liquid container I28. An inverted bell I29 is mounted in vessel I28 and has a connection I30 with the weighbeam I00 on the side of the weighbeam pivot IIJI adjacent the inverted bell I04. A bleed line I33 extends from the stabilizing chamber I26 and has an adjustable valve I32 interposed therein.

Assuming that the device of Fig, 9 is intended for a draft installation having predominant storage lag, it will be seen that when a condition of unbalance, as between the inverted bell I04 and the loading element I02 occurs, the weighbeam I00 will pivot commensurate to the variation and cause the valve plunger II I to be deflected. If this deflection is caused by a reduction in draft which permits loading element I02 to force the piston plunger downwardly, connection will be established between the compressed air line H2 and the line II3 connected with the lower end of the power cylinder II1. This will in turn cause an upward movement of the power piston IIB and raise the stabilizing cylinder I23 thereby creating a sub-atmospheric condition in the stabilizing cylinder I23, line I24, stabilizing chamber I26 and inverted bell I29 which complements the reduction in draft effect upon the inverted I04, said inverted bell I20 extending into piston III to neutral position as shown.

' The new setting'of the damper I2I increases the draft, and as the draft effect is increasing and i'. being transmitted to inverted bell I04 through line I08, the pressure condition in the stabilizing chamber I28 and connected parts is being dissipated by intake of air at conduit l3l under the control of the valve I32. The valve setting will determine the rate of air intake, and hence compensate for the storage lag as will be obvious.

It will readily be seen that in addition to the non-electrical character of the device, this embodiment diflers from previous embodiments by the introduction into the system of the secondary stabilizing inverted bell I23 which constitutes an element separate from the metering unit I04, but acts upon the weighbeam I to complement either the metering unit I04 or the loading unit I02 according to the condition of the variation in the process to be controlled.

In Fig. 10 a system somewhat similar to that in Fig. 9, but operating electrically is disclosed. In this system the metering unit constitutes the inverted bell I04 mounted in the liquid vessel I controlled by the line I08. Bell I04 has c0nnection I03 with weighbeam I00 which is pivoted intermediate its ends at IOI, and has a loading element I02 acting upon its opposite end. A

bell I28 is connected at I30 the metering unit a liquid vessel I28 with which a stabilizing conduit I21 communicates. The weighbeam I00 is interposed in a suitable electrical system for which purpose it mounts contacts I40 with respect to'which switch elements I and I42 are positioned on opposite sides of the weighbeam and in the path of travel thereof. said switch elements I-4I, I42 preferably being flexible and being electrically connected by means of leads I43 and I44, respectively, of an electric positioning motor I45 which has another lead-I48 connected with a source of current I41, said lead I48 being grounded at. I48. The circuit to the weighbeam is completed through line I48 grounded at I50. Positioning motor I45 has an operating shaft I5I on which is mounted an arm I52 connected with a suitable member I53 adapted for connection with a control element in the process to be controlled, such for example asa damper. Shaft I5I also mounts an arm I54 which has connected thereto a suitable rod carrying a piston I55 mounted in a stationary cylinder I58 open to atmosphere at one end. A line I51 extends from the closed end of cylinder I58 to a stabilizing chamber I58 which is in turn connected with the stabilizing bell I29 by conduit I21. Stabilizing chamber I58 has a conduit I50 open to atmosphere with a. control valve I80 interposed therein.

The operation of this device is the same as in stabilizing inverted with the weighbeam adjacent the preferred device, it being understood that when the weighbeam I00 is unbalanced, contact will be made with one of the switch elements I4 I,

- I42, andthe motor caused to operate in a direction to control the power member I53, and also to actuate the piston I55 for the purpose of creating a stabilized pressure condition in stabilizing bell I28 and stabilizing chamber I58.

The operation of bleed of the stabilizing system at conduit I58 controlled by valve I80 occurs after the weighbeam is restored to balance with the valve I being set to compensate for the storage lag in the process being controlled.

We claim: 1. Incombination, a floating regulator including an element responsive to fluid pressure and adapted to be actuated in response to a variable element of a process to be controlled, means for connecting said regulator with said element, an electrical power unit controlled by the pressure responsive element of said regulator, a stabilizer for said regulator comprising a fluid pressure generator actuated and controlled solely by said power unit, means applying pressure from said generator to said pressure responsive element, whereby said fluid pressure constitutes the sole means opposing the initial actuating variation to restore said regulator to balance, and means for bleeding oil said fluidpressure.

2. In combination, a normally balanced regulator including a diaphragm and adapted to be actuated in response to an unbalancing variation in either of two elements of a process to be controlled, means for connecting said regulator with said elements, an electrical power unit con-- trolled by said regulator diaphragm for actuating a control element of the process to be controlled, a fluid pressure generator actuated and controlled solely by said power unit, means for impressing said fluid pressure in rebalancing relation upon the diaphragm, said fluid pressure constituting the sole means to rebalance the regulator, and means for dissipating said fluid pressure at a controlled rate during reestablishment of a balanced condition in the first mentioned elements.

3. The combination with a normally balanced regulator comprising a housing having 8. diaphragm, a fluid linev communicating with said housing on one side of said diaphragm, a piv oted lever actuated by said diaphragm, electrical switch means controlled by said lever, a reversible electric power member controlled by said switch means, mean normally balancing the pressure in said line for maintaining said diaphragm in neutral position. said diaphragm being shifted responsive to variations either in said last named means or in said fluid line, of a fluid pressure generator actuated by said power member, means for impressing the pressure condition created by said generator upon said diaphragm to rebalance said diaphragm, and means for dissipating said fluid pressure from said. generator while equilibrium is restored between the pressure in said line and said balancing means responsive to operation of said power member.

4. In combination, a normally balanced regulator including a diaphragm and adapted to be actuated in response to an unbalancing variation in an element of a process to be regulated, means for connecting said regulator with said element, an electrical power unit controlled by said regulator for actuating said control element of the process to be regulated, a cylinder, -a piston shiitable in said cylinder by said power unit,

- other direction, and

trol valve regulating air flow through said conduit, a power unit controlled for operation in either of two directions by said regulator and adapted to actuate said control element 0! the process to be regulated, a pneumatic pump actuated by said powerunit to create a positive air pressure upon operation in one direction and a negative air pressure upon operation in the a conduit connecting said pump and a point of said first conduit between said valve and said regulator.

,6. In combination, a regulator including a chamber containing a diaphragm and having difierential pressure connections on opposite sides of the diaphragm, means for connecting said regulator with variable means normally balancing said diflerential pressure, a reversible power unit controlled by said regulator diaphragm, a fluid pressure system connected with said diaphragm chamber on the metering side 20 thereof, and means actuated by said power unit for creating and temporarily maintaining a pressure condition in said system stabilizing said regulator and rebalancing said diaphragm after deflection or said diaphragm.

'I. In combination, a normally balanced regulator including a diaphragm and adapted to be actuated in response to an unbalancing variation in an element of a process to be regulated, means for connecting said regulator with said element, an electrical power unit controlled by said regulator diaphragm for ment of the proces to be regulated, a cylinder, a piston shiitable in said cylinder by said power unit, a stabilizing chamber open to atmosphere,

a valve restricting said opening to atmosphere,

and a fluidllne connecting said cylinder, chamber and regulator.

FRANK DONALD BURNS. WARREN B. 'I'HORNE.

actuating said control ele- 

